US4362339A - Hydraulic brake system with an antiskid control apparatus - Google Patents

Hydraulic brake system with an antiskid control apparatus Download PDF

Info

Publication number
US4362339A
US4362339A US06/227,895 US22789581A US4362339A US 4362339 A US4362339 A US 4362339A US 22789581 A US22789581 A US 22789581A US 4362339 A US4362339 A US 4362339A
Authority
US
United States
Prior art keywords
pressure
piston
fluid
master cylinder
valve device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/227,895
Other languages
English (en)
Inventor
Juan Belart
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ITT Inc
Original Assignee
ITT Industries Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ITT Industries Inc filed Critical ITT Industries Inc
Assigned to ITT INDUSTRIES, INC., A CORP. OF DE reassignment ITT INDUSTRIES, INC., A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BELART JUAN
Application granted granted Critical
Publication of US4362339A publication Critical patent/US4362339A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/44—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition co-operating with a power-assist booster means associated with a master cylinder for controlling the release and reapplication of brake pressure through an interaction with the power assist device, i.e. open systems
    • B60T8/445—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition co-operating with a power-assist booster means associated with a master cylinder for controlling the release and reapplication of brake pressure through an interaction with the power assist device, i.e. open systems replenishing the released brake fluid volume into the brake piping

Definitions

  • the present invention relates to a hydraulic brake system comprising an antiskid control apparatus, a master cylinder and at least one wheel cylinder, with the wheel cylinder being adapted to be connected to the master cylinder or a fluid outlet via antiskid control valves.
  • Brake systems of this type are known, for example, from the magazines "Automobil-Technik” of Oct. 30, 1978, pages 28 to 30, and "Automobiltechnische Zeitschrift” 81 (1979) 5, pages 201 to 208.
  • brake systems are described in which a recirculating pump feeds the fluid returned to the master cylinder pressure chamber under high pressure.
  • a recirculating pump feeds the fluid returned to the master cylinder pressure chamber under high pressure.
  • the fluid volume returned causes a volume increase in the master cylinder pressure chamber.
  • This volume increase in the pressure chamber resets the master cylinder piston, the brake pedal moves in opposition to its actuating direction.
  • Such pulsating brake pedal movements by no means appeal to the vehicle operator, they impair the pedal feeling considerably and affect the application of a dosed brake pressure adversely.
  • a feature of the present invention is the provision of a hydraulic brake system having an antiskid control apparatus comprising a master brake cylinder; a fluid return line; at least one wheel brake cylinder; antiskid control valves coupled to the master cylinder, the wheel cylinder and the return line to connect the wheel cylinder to one of the master cylinders and the return line; and a valve device coupled to a fluid source, the master cylinder and the return line to deliver fluid from the fluid source to the wheel brake cylinder through at least one check valve opening in opposition to master cylinder pressure, the valve device being controlled by a piston having a first end surface acted upon by the master cylinder pressure in the sense of opening the valve device and a second end surface acted upon by the pressure of the fluid of the source in the sense of closing the valve device.
  • the above arrangement causes the required fluid to be supplied through the check valve rather than being withdrawn from the master cylinder.
  • the valve device By arranging the valve device to be controlled by a piston acted upon by hydraulic pressure, it is achieved that the fluid pressure present at the check valve is adapted to the pressure in the master cylinder. Therefore, during normal brake application, the fluid pressure present at the check valve approximates the pressure in the master cylinder, conditioned by the piston acted upon by pressure. Only when the pressure in the master cylinder drops can the check valve open, enabling the required fluid volume to be supplied to the master cylinder directly. The decrease in the fluid pressure acting on the check valve is accomplished via the master cylinder.
  • the fluid source will deliver fluid only on actuation of the master cylinder.
  • Such control elements may shut off the drive for the fluid source by electrical and/or mechanical means.
  • the fluid source is a fluid accumulator whose fluid flow to the valve device is ducted through a valve opening at the beginning of a braking action and closing on termination of a braking action, a constant-pressure fluid volume may be withdrawn by the brake system at all times.
  • controlled delivery of fluid to the brake system is possible via a favorably constructed valve in which the piston acts as a valve slide, with the fluid admitted through the inlet located in the housing being deliverable to the outlet of the valve device through a channel system in the piston, or the inlet being adapted to be closed by the piston.
  • the pressure chamber bounded by the second end surface of the piston and the housing communicates with the outlet of the valve device through a channel in the piston. This avoids the need for an external pressure pipe.
  • the pressure chamber as an outlet chamber, the space additionally provided as the outlet chamber is no longer necessary, the valve device becomes simpler per se and thus more economical.
  • valve device which is controlled electro-magnetically and/or hydraulically. If a valve is provided which is adapted to be driven by an electric pulse and returns to its closed state in the presence of specific hydraulic conditions, this valve may be opened by a control signal of the antiskid control apparatus and closed again with the master cylinder in the unpressurized state. By controlling the fluid flow in such a manner, it is achieved that the valve device is actuated only on demand, thereby precluding fluid losses in the valve device with no fluid flow required.
  • the pump system charges the pressure accumulator when the vehicle is started, after which it is only required to compensate for the very minor losses of the pressure accumulator.
  • the pump drive is actuated relatively rarely, resulting in energy savings.
  • FIG. 1 is a schematic diagram of a power-assisted hydraulic brake system in accordance with the principles of the present invention.
  • FIG. 2 is a longitudinal cross-sectional view of a modified valve device that may be employed in the hydraulic brake system of FIG. 1.
  • reference number 1 designates a master cylinder and reference number 2 designates a vacuum brake booster inserted upstream from master cylinder 1.
  • vacuum brake booster 2 Via a port 4, vacuum brake booster 2 is connected to a vacuum source providing the power assistance.
  • the arrangement comprising vacuum brake booster 1 and master cylinder 1 connected downstream therefrom is controlled by a brake pedal 3.
  • Mounted on master cylinder 1 is a fluid reservoir 5 which is connected to pressure chambers 6 and 7 of master cylinder 1 through breather bores not shown.
  • Fluid reservoir 5 is preferably subdivided into three compartments 8, 9 and 10 which are interconnected by overflow pipes.
  • compartment 8 is assigned to pressure chamber 6 via a breather bore
  • compartment 9 to chamber 7 via another breather bore
  • compartment 10 serves as a sump which via a pump 12 feeding the fluid into a pressure accumulator 11.
  • the master cylinder chambers are connected to the brake actuating members 17 to 20 of vehicle wheels 13 to 16. Via a pressure line 21 and a solenoid valve 22 which is open in the de-energized state, pressure chamber 6 supplies pressure to wheel cylinders 19, 20 of rear wheels 15, 16. Via line 23 and solenoid valves 24 and 25 which are open in the de-energized state, pressure chamber 7 supplies pressure to brake-actuating members 17 and 18 of front wheels 13 and 14.
  • a solenoid valve 26 which is closed in the de-energized state and connects, in the event of a desired pressure decrease in the brake-actuating members 19 and 20, these actuating members to an unpressurized collector line 27 which connects with a port 29 of fluid reservoir 5 via a return line 28.
  • brake-actuating members 17 and 18 of the front wheels 13 and 14 are connected separately to collector line 27 via solenoid valves 30 and 31, respectively, which are closed in the de-energized state. This makes it possible to increase or decrease the pressures in brake-actuating members 17 and 18 of the front wheels to different magnitudes separately from each other whereas the pressures in the brake-actuating members 19 and 20 of the rear wheels can only be changed jointly.
  • Solenoid valves 22, 24 to 26, 30 and 31 are controlled by an antiskid control apparatus not shown, receiving their information from sensors associated with the wheels.
  • the antiskid control apparatus will detect an imminent locked condition of a wheel in time for it to actuate the relevant solenoid valves in order to withdraw pressurized fluid from the associated brake-actuating member and thus lower the pressure.
  • the antiskid control apparatus may undertake another pressure increase in the appropriate brake actuating member.
  • valves 22, 24 and 25 which are open in the de-energized state are conventionally constructed such that in the open state only one direction of flow is allowed, or only one direction of flow should be preferably used, each of them is connected in parallel with an associated check valve 32 opening in opposition to the pressure of pressure chambers 6 and 7. In this manner it is ensured that upon termination of a braking action the pressure in wheel cylinders 17 to 20 is allowed to decrease via the associated check valves 32, pressure chambers 6 and 7 and the breather bores of reservoir 5.
  • a pressure accumulator 11 Allocated to the brake system described so far is a pressure accumulator 11 which is charged by pump 12 via check valve 33.
  • Suction port 34 of pump 12 communicates with compartment 10 of fluid reservoir 5.
  • a filter 35 is inserted in suction port 34.
  • suction port 34 it is possible to provide in suction port 34 a check valve 36 opening in the direction of pump 12 in order to prevent fluid from being fed in the direction of fluid reservoir 5.
  • valve device 37 which is a pressure-relief valve and with accumulator 11 fully charged returns any excess of fluid supplied to return line 28 via line 38.
  • a check valve 39 opening in the direction of return line 28 is provided between collector line 27 and return line 28.
  • Drive unit 40 for pump 12 may, for example, be the engine of the automotive vehicle. For this purpose, it will be an advantage to flange pump 12 directly to a rotating part of the engine.
  • drive unit 40 for pump 12 could be an electric motor rather than the vehicle engine which is actuated in response to the pressure prevailing in pressure accumulator 11.
  • the instantaneous pressure of accumulator 11 is signalled via a control line 42 to a pressure switch 41 which actuates the electric motor of drive unit 40 via an electric control line 43.
  • pressure switch 41 requires a hysteresis permitting pressure fluctuations in accumulator 11 of about 30 bars.
  • the minimum accumulator pressure could be fixed at 140 bars and the maximum pressure at 170 bars.
  • accumulator 11 Via a pressure line 44 and a solenoid valve 46 which is closed in the de-energized state, accumulator 11 communicates with the inlet 47 of a valve device 45. Valve 46 which is closed in the de-energized state is connected to outlet 49 of valve device 45 via a hydraulic control line 48. Valve 46 which is closed when de-energized is opened under electrical control and will not close until after outlet 49 is unpressurized and this condition has been signalled to the open valve 46 via hydraulic control line 48.
  • Valve device 45 includes a piston 50 which acts as a hydraulically operated valve member between inlet 47 and outlet 49 in the sense of a pressure reduction.
  • piston 50 is a stepped piston having its first end surface 51 exposed to the pressure of pressure chamber 7. Since piston 50 is sealed to and slides in the housing of valve device 45, outlet 49 is formed at the step 53 between piston 50 and the housing of valve device 45, this outlet communicating with pressure lines 21 and 23, and thus, with pressure chambers 6 and 7 via check valves 55 and 56, respectively.
  • check valves 55 and 56 are arranged to be openable in opposition to the pressure of pressure chambers 6 and 7.
  • Outlet 49 is connected to the pressure chamber 57 bounded by the housing of valve device 45 and piston 50 via an axial channel 67 so that the second end surface 52 of piston 50 is acted upon by the pressure of outlet 49.
  • Radial bore 68 and inlet 47 will overlap to a greater or lesser extent in accordance with the position of piston 50 so that, dependent on the piston position, a pressure will build up in outlet 49 which, starting from zero pressure, may increase up to the pressure of accumulator 11.
  • a stop 58 which limits the open position of piston 50, and thereby provides a defined open condition of the controlled system.
  • a stop 60 in pressure chamber 59 which is bounded by end surface 51 of piston 50 in order to be able to limit the closed position of piston 50.
  • a pressure outlet 61 which is connected to the unpressurized fluid reservoir 5 via line 62, line 38 and return line 28.
  • pressure outlet 61 is closed by piston 50.
  • Piston 50 acts as a valve slide for pressure outlet 61.
  • the mode of operation of the arrangement of FIG. 1 is as follows.
  • brake pedal 3 causes actuation of vacuum brake booster 2, its output force being transmitted to master cylinder 1.
  • pressure chambers 6 and 7 a pressure will build up which travels down to brake-actuating members 17 to 20 through lines 21 and 23.
  • the antiskid control apparatus (not shown) detects an imminent locked condition of a wheel during a braking action, it will close the associated pressure inlet valve 22, 24 and 25 (open in the de-energized state) and open the associated pressure outlet valve 26, 30 and 31 (closed in the de-energized state) in accordance with the wheel rotational behavior.
  • the pressure in the associated wheel cylinder will drop, the wheel being allowed to accelerate again and leave the danger zone in which it may become locked.
  • piston 50 On attainment of the pressure prevailing in pressure chamber 7, however, piston 50 will assume a pressure-balanced state because the pressure acting on end surface 51 is equal to the pressure acting on annular surface 54 in outlet 49 and on end surface 52. Any further, minor, pressure increase will immediately cause a displacement of piston 50 to the left, thus moving radial channel 68 away from under inlet 47 so that inlet 47 will be closed by piston 50. Should the pressure increase have been greater than the pressure prevailing in pressure chamber 7, piston 50 will be shifted an amount sufficient to enable the excess pressure to escape through pressure outlet 61, i.e., piston 50 will assume a defined position with the pressure in pressure chamber 7 constant. The pressure thus metered into outlet 49 corresponds to the pressure in pressure chamber 7 and acts on the relevant pressure chambers 6 and 7 directly via check valves 55, 56.
  • the antiskid control apparatus which then establishes that the wheel concerned has largely recovered, will again close the associated one of outlet valves 26, 30 and 31, and open the associated one of inlet valves 22, 24 and 25.
  • a substantial amount of fluid will be required to flow through the associated pressure line in order to adapt the pressure in the associated brake-actuating member to the pressure in the other brake-actuating members.
  • this fluid requirement will not be withdrawn from the relevant one of pressure chambers 6 and 7 of master cylinder 1, but rather will enter the associated brake circuit via check valves 55 and 56.
  • the vehicle operator who depresses brake pedal 3 will hardly, if at all, be able to notice this fluid flow in the relevant brake circuit by a different pedal feeling. It is insured in this manner that master cylinder 1 fluid volume cannot become exhausted, no matter how many control cycles are performed.
  • valve 46 which is closed when de-energized will remain open because it is not allowed to return to the closed state until outlet 49 is unpressurized. This, however, will be the case only if the vehicle operator releases brake pedal 3 and the braking action is terminated. In this case, the pressure acting on end surface 51 of piston 50 will drop to zero, and the pressure acting on end surface 52 and annular surface 54 will immediately displace the piston to the left, closing inlet 47 and opening pressure outlet 61 fully. There will thus occur a prompt pressure decrease in outlet 49. This will be signalled to valve 46 via hydraulic control line 48 so that it will return again to its closed rest position.
  • valve operation described so far is presented in a highly simplified form in order to make the arrangement more clearly understood.
  • piston 50 will reciprocate continuously in order to compensate for the respective pressure fluctuations to maintain a constant output pressure.
  • this valve device will operate in a manner similar to constructions known in the art.
  • the antiskid control apparatus will be disabled, making normal braking of the device possible.
  • valve 46 which is closed when de-energized cannot open with the operation of the brake system continuing.
  • FIG. 2 shows a more favorable embodiment of a valve device 45 of FIG. 1.
  • a simple piston 50' slides in a housing of valve device 45', and end surfaces 51 and 52 are again exposed to pressure in accordance with the description given above.
  • pressure outlet 49 is located in pressure chamber 57 which is adapted to be connected to the inlet through channels 67 and 68.
  • Check valve 56 is preferably inserted in an extended bore 63 provided in end surface 51, with bore 63 communicating with channel 67.
  • a spring 64 bearing against a circlip 65 provided in extended bore 63 holds a ball 66 in sealing engagement with a valve seat formed by the channel orifice in bore 63.
  • FIG. 1 shows a more favorable embodiment of a valve device 45 of FIG. 1.
  • this embodiment dispenses with the need for an external check valve so that additional fluid ports are avoided which, as sources of errors, might cause a failure of the valve device. Further, this valve device permits a particularly small and accordingly compact design which makes it advantageously suitable for use in a bulky antiskid control apparatus.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
US06/227,895 1980-03-20 1981-01-23 Hydraulic brake system with an antiskid control apparatus Expired - Fee Related US4362339A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803010639 DE3010639A1 (de) 1980-03-20 1980-03-20 Hydraulisches bremssystem mit einer antiblockierregelanlage
DE3010639 1980-03-20

Publications (1)

Publication Number Publication Date
US4362339A true US4362339A (en) 1982-12-07

Family

ID=6097730

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/227,895 Expired - Fee Related US4362339A (en) 1980-03-20 1981-01-23 Hydraulic brake system with an antiskid control apparatus

Country Status (8)

Country Link
US (1) US4362339A ( )
JP (1) JPS56131447A ( )
DE (1) DE3010639A1 ( )
ES (1) ES500481A0 ( )
FR (1) FR2478560A1 ( )
GB (1) GB2072283B ( )
IT (1) IT1139320B ( )
SE (1) SE8100682L ( )

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4440454A (en) * 1980-10-28 1984-04-03 Itt Industries, Inc. Pressure control arrangement for vehicle braking system with antiskid control equipment
US4492413A (en) * 1980-10-28 1985-01-08 Itt Industries, Inc. Control arrangement for an antiskid hydraulic braking system of a vehicle
US4523792A (en) * 1982-12-22 1985-06-18 Itt Industries, Inc. Dual-circuit hydraulic brake system
US4523791A (en) * 1982-08-28 1985-06-18 Itt Industries, Inc. Method for monitoring and controlling hydraulic brake slip control devices supplied with energy from an external source, and an apparatus for implementing this method
US4685747A (en) * 1985-01-25 1987-08-11 Alfred Teves Gmbh Brake system with slip control
US4807944A (en) * 1986-07-22 1989-02-28 Alfred Teves Gmbh Brake system with anti-lock control and traction slip control
US4826258A (en) * 1986-10-15 1989-05-02 Alfred Teves Gmbh Anti-lock brake system with traction slip control
US4828336A (en) * 1986-09-04 1989-05-09 Alfred Teves Gmbh Skid-controlled brake system
US4834465A (en) * 1986-12-26 1989-05-30 Messier-Hispano-Bugatti Hydraulic braking circuit for an aircraft
US4842340A (en) * 1987-04-30 1989-06-27 Alfred Teves Gmbh Brake for a vehicle trailer
US4902077A (en) * 1983-06-30 1990-02-20 Alfred Teves, Gmbh Hydraulic brake system
US4971403A (en) * 1988-08-20 1990-11-20 Wabco Westinghouse Fahrzeugbremsen Gmbh Power brake for an anti-lock hydraulic brake system
US5174637A (en) * 1989-07-27 1992-12-29 Bendix Europe Services Techniques Hydraulic braking circuit
US5303990A (en) * 1991-07-03 1994-04-19 Tokico Ltd. Brake fluid pressure control apparatus
US5472268A (en) * 1992-10-14 1995-12-05 Tokico Ltd. Brake fluid pressure control apparatus for antiskid control and traction control

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3040601A1 (de) * 1980-10-29 1982-05-27 Alfred Teves Gmbh, 6000 Frankfurt Hydraulische bremsanlage mit einer bremsschlupfregelanlage
US4453782A (en) * 1980-11-29 1984-06-12 Nippon Air Brake Co., Ltd. Brake fluid pressure control apparatus in skid control system
DE3317629A1 (de) * 1983-05-14 1984-11-15 Alfred Teves Gmbh, 6000 Frankfurt Verfahren zur steuerung einer schlupfgeregelten bremsanlage und vorrichtung zur durchfuehrung des verfahrens
DE3342908A1 (de) * 1983-11-26 1985-06-05 Alfred Teves Gmbh, 6000 Frankfurt Schlupfgeregelte bremsanlage fuer kraftfahrzeuge
DE3404135A1 (de) * 1984-02-07 1985-08-14 Daimler-Benz Ag, 7000 Stuttgart Einrichtung zur nachspeisung von bremsfluessigkeit
DE3426455A1 (de) * 1984-07-18 1986-01-30 Alfred Teves Gmbh, 6000 Frankfurt Schlupfgeregelte bremsanlage fuer kraftfahrzeuge
DE3511533A1 (de) * 1985-03-29 1986-10-09 Alfred Teves Gmbh, 6000 Frankfurt Bremsanlage fuer kraftfahrzeuge
DE3527190A1 (de) * 1985-07-30 1987-02-12 Teves Gmbh Alfred Bremsanlage mit schlupfregelung
DE3602741A1 (de) * 1986-01-30 1987-08-06 Teves Gmbh Alfred Bremsanlage mit schlupfregelung
DE3603079A1 (de) * 1986-02-01 1987-08-06 Teves Gmbh Alfred Hydraulische speicherlose schlupfgeregelte bremsanlage
DE3704623A1 (de) * 1986-02-14 1987-10-29 Aisin Seiki Antiblockiervorrichtung fuer ein kraftfahrzeug
DE3627000C2 (de) * 1986-08-08 1998-05-20 Teves Gmbh Alfred Bremsanlage mit Schlupfregelung
US4844558A (en) * 1986-09-19 1989-07-04 Nippon Abs, Ltd. Brake fluid pressure control apparatus in skid control system
JPS6378859A (ja) * 1986-09-24 1988-04-08 Aisin Seiki Co Ltd アンチスキツド装置
DE3705311C2 (de) * 1987-02-19 1998-08-20 Teves Gmbh Alfred Mehrkreisige hydraulische Bremsanlage für Kraftfahrzeuge
JPH0611269Y2 (ja) * 1987-05-29 1994-03-23 アイシン精機株式会社 液圧ブレ−キ装置
JP2650912B2 (ja) * 1987-06-11 1997-09-10 曙ブレーキ工業株式会社 車両用のアンチロツク装置
JP2767246B2 (ja) * 1987-11-02 1998-06-18 日本エービーエス株式会社 アンチスキッド装置用液圧制御装置
DE3842699C2 (de) * 1988-12-19 1997-04-17 Teves Gmbh Alfred Blockiergeschützte hydraulische Bremsanlage
DE3922082A1 (de) * 1988-12-19 1991-01-17 Teves Gmbh Alfred Blockiergeschuetzte hydraulische bremsanlage
US5255963A (en) * 1989-08-09 1993-10-26 Robert Bosch Gmbh Hydraulic vehicle brake system with anti-skid apparatus
DE4106790A1 (de) * 1990-07-26 1992-09-10 Teves Gmbh Alfred Blockiergeschuetzte, hydraulische bremsanlage
DE4134445A1 (de) * 1991-10-18 1993-04-22 Teves Gmbh Alfred Blockiergeschuetzte hydraulische bremsanlage
DE4244675C2 (de) * 1991-11-07 1998-10-29 Tokico Ltd Antiblockiersystem
US5397175A (en) * 1992-03-06 1995-03-14 Tokico Ltd. Fluid pressure control apparatus for antiskid brakes
DE19534221A1 (de) * 1995-09-15 1997-03-20 Teves Gmbh Alfred Hydraulische Bremsanlage für Kraftfahrzeuge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3514161A (en) * 1968-06-11 1970-05-26 Goodyear Tire & Rubber Brake pressure control valve
US3671085A (en) * 1970-10-12 1972-06-20 Gen Motors Corp Antilock brake modulator
US3702713A (en) * 1970-09-16 1972-11-14 Itt Anti-skid control device
US4168100A (en) * 1976-08-13 1979-09-18 Nissan Motor Company, Limited Anti skid control unit

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2519835C2 (de) * 1975-05-03 1986-07-10 Alfred Teves Gmbh, 6000 Frankfurt Sicherheitseinrichtung für eine hydraulische blockiergeschützte Fahrzeugbremsanlage
GB1567066A (en) * 1976-08-13 1980-05-08 Nissan Motor Anti skid control unit
DE2644659C2 (de) * 1976-10-02 1986-07-10 Alfred Teves Gmbh, 6000 Frankfurt Vorrichtung für hydraulische Bremssysteme mit Blockierschutz
FR2402556A1 (fr) * 1977-09-09 1979-04-06 Dba Systeme de freinage antipatinant comportant un dispositif de realimentation de fluide et dispositif de realimentation pour un tel systeme
US4182536A (en) * 1978-04-03 1980-01-08 The Bendix Corporation Adaptive braking modulator valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3514161A (en) * 1968-06-11 1970-05-26 Goodyear Tire & Rubber Brake pressure control valve
US3702713A (en) * 1970-09-16 1972-11-14 Itt Anti-skid control device
US3671085A (en) * 1970-10-12 1972-06-20 Gen Motors Corp Antilock brake modulator
US4168100A (en) * 1976-08-13 1979-09-18 Nissan Motor Company, Limited Anti skid control unit

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4492413A (en) * 1980-10-28 1985-01-08 Itt Industries, Inc. Control arrangement for an antiskid hydraulic braking system of a vehicle
US4440454A (en) * 1980-10-28 1984-04-03 Itt Industries, Inc. Pressure control arrangement for vehicle braking system with antiskid control equipment
US4523791A (en) * 1982-08-28 1985-06-18 Itt Industries, Inc. Method for monitoring and controlling hydraulic brake slip control devices supplied with energy from an external source, and an apparatus for implementing this method
US4523792A (en) * 1982-12-22 1985-06-18 Itt Industries, Inc. Dual-circuit hydraulic brake system
US4902077A (en) * 1983-06-30 1990-02-20 Alfred Teves, Gmbh Hydraulic brake system
US4685747A (en) * 1985-01-25 1987-08-11 Alfred Teves Gmbh Brake system with slip control
US4807944A (en) * 1986-07-22 1989-02-28 Alfred Teves Gmbh Brake system with anti-lock control and traction slip control
US4828336A (en) * 1986-09-04 1989-05-09 Alfred Teves Gmbh Skid-controlled brake system
US4826258A (en) * 1986-10-15 1989-05-02 Alfred Teves Gmbh Anti-lock brake system with traction slip control
US4834465A (en) * 1986-12-26 1989-05-30 Messier-Hispano-Bugatti Hydraulic braking circuit for an aircraft
US4842340A (en) * 1987-04-30 1989-06-27 Alfred Teves Gmbh Brake for a vehicle trailer
US4971403A (en) * 1988-08-20 1990-11-20 Wabco Westinghouse Fahrzeugbremsen Gmbh Power brake for an anti-lock hydraulic brake system
US5174637A (en) * 1989-07-27 1992-12-29 Bendix Europe Services Techniques Hydraulic braking circuit
US5303990A (en) * 1991-07-03 1994-04-19 Tokico Ltd. Brake fluid pressure control apparatus
US5312175A (en) * 1991-07-03 1994-05-17 Tokico Ltd. Brake fluid pressure control apparatus
US5335982A (en) * 1991-07-03 1994-08-09 Tokico Ltd. Brake fluid pressure control apparatus
US5472268A (en) * 1992-10-14 1995-12-05 Tokico Ltd. Brake fluid pressure control apparatus for antiskid control and traction control

Also Published As

Publication number Publication date
JPH0130661B2 ( ) 1989-06-21
FR2478560A1 (fr) 1981-09-25
DE3010639A1 (de) 1981-09-24
JPS56131447A (en) 1981-10-15
IT8120582A0 (it) 1981-03-19
ES8202514A1 (es) 1982-02-01
GB2072283B (en) 1983-10-19
GB2072283A (en) 1981-09-30
IT1139320B (it) 1986-09-24
FR2478560B1 ( ) 1984-12-28
ES500481A0 (es) 1982-02-01
SE8100682L (sv) 1981-09-21
DE3010639C2 ( ) 1989-10-26

Similar Documents

Publication Publication Date Title
US4362339A (en) Hydraulic brake system with an antiskid control apparatus
US4790608A (en) Skid-controlled brake system with master cylinder pistons and with plungers supported on stationary transverse member
US4685747A (en) Brake system with slip control
US4826255A (en) Anti-lock brake system with variable delivery pump controlled in response to detected position of master cylinder piston and method therefor
US5002345A (en) Hydraulic brake system for automotive vehicles
US4804236A (en) Hydraulic brake system with anti-skid control and/or traction slip control
US20090033146A1 (en) Method and device for operating a hydraulic vehicle brake system
US4840436A (en) Anti-lock brake system with traction slip control
US5938297A (en) Method and device for brake application
EP0448031A1 (en) Brake pressure generator
US6450589B2 (en) Brake pressure transducer for a hydraulic vehicle brake system
US4825989A (en) Anti-lock brake system with clutch or transmission control
US4586591A (en) Pressure-fluid-operable vehicle brake system
US4643488A (en) Hydraulic vehicle servo brake
US4340257A (en) Hydraulic brake system
US3782781A (en) Single fluid booster and system
US5564798A (en) Anti-locking hydraulic brake system
US4759591A (en) Hydraulic brake system
KR20010006505A (ko) 유압 차량 브레이크 시스템용 브레이크-압력-전달 장치 및 그를 구비한 브레이크 시스템
US5154495A (en) Process (of) for operating a master cylinder
JPS62253555A (ja) 液圧ブレ−キシステム
US5129714A (en) Anti-lock hydraulic brake system with hydraulically controlled inlet valve
US4319455A (en) Hydraulic power brake system and hydraulic brake booster and controls therefor
US5137339A (en) Regulator supply valve for adaptive braking and traction control systems
JPH05505783A (ja) アンチロック制御付油圧ブレーキシステム

Legal Events

Date Code Title Description
MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, PL 96-517 (ORIGINAL EVENT CODE: M170); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 4

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, PL 96-517 (ORIGINAL EVENT CODE: M171); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 8

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FEPP Fee payment procedure

Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

LAPS Lapse for failure to pay maintenance fees
FP Lapsed due to failure to pay maintenance fee

Effective date: 19941207

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362